US20030173428A1 - Fuel-injection valve for internal combustion engines - Google Patents
Fuel-injection valve for internal combustion engines Download PDFInfo
- Publication number
- US20030173428A1 US20030173428A1 US10/296,712 US29671203A US2003173428A1 US 20030173428 A1 US20030173428 A1 US 20030173428A1 US 29671203 A US29671203 A US 29671203A US 2003173428 A1 US2003173428 A1 US 2003173428A1
- Authority
- US
- United States
- Prior art keywords
- valve
- valve member
- sealing face
- embodied
- fuel
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000002347 injection Methods 0.000 title claims abstract description 44
- 239000007924 injection Substances 0.000 title claims abstract description 44
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 27
- 238000007789 sealing Methods 0.000 claims abstract description 43
- 239000000446 fuel Substances 0.000 claims abstract description 35
- 230000007704 transition Effects 0.000 claims description 7
- 230000000694 effects Effects 0.000 description 2
- 239000003344 environmental pollutant Substances 0.000 description 2
- 231100000719 pollutant Toxicity 0.000 description 2
- 230000005489 elastic deformation Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/047—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves being formed by deformable nozzle parts, e.g. flexible plates or discs with fuel discharge orifices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
Definitions
- the invention is based on a fuel injection valve for internal combustion engines of the kind known for instance from German Patent Disclosure DE 196 18 650 A1.
- a fuel injection valve has a valve body, in which a bore is embodied.
- a pistonlike valve member is disposed longitudinally displaceably in this bore and on its end toward the combustion chamber has a valve sealing face, which cooperates with a valve seat embodied on the end of the bore toward the combustion chamber.
- the valve member is surrounded by a pressure chamber embodied in the valve body, and this pressure chamber can be filled with fuel at high pressure and extends as far as the valve seat.
- At least one injection opening is embodied in the valve seat, which connects the bore and thus the pressure chamber with the combustion chamber of the engine.
- valve member By means of a longitudinal motion of a valve member, the valve member with its valve sealing face lifts from the valve seat, causing the pressure chamber to communicate with the injection openings.
- the valve seat is embodied essentially conically, and the tip of the cone forming the conical face is oriented toward the combustion chamber.
- the valve sealing face of the valve member is correspondingly embodied conically as well, and the valve sealing face has two conical faces with different angles of inclination, so that at the transition between these two conical faces, a sealing edge is formed. In the closing position of the valve member, or in other words when the valve sealing face is resting on the valve seat, this sealing edge is pressed into the valve seat, so that secure sealing off of the pressure chamber from the injection openings is possible.
- the valve member is acted upon by a device with a closing force that presses the valve member onto the valve seat. Because of the hydraulic pressure in the pressure chamber, the valve member experiences a force acting in the axial direction, which force is oriented counter to the closing force. If the pressure in the pressure chamber exceeds an opening pressure, then the hydraulic force on the valve member becomes greater than the closing force, and the valve member moves out of its closing position, away from the valve seat. The magnitude of this opening pressure depends, among other factors, on what the diameter of the sealing edge at the valve seat is. A change in the opening pressure causes a change in the injection characteristic of the injection valve, so that for optimal injection, an at least approximately constant opening pressure is indispensable.
- the known fuel injection valve has the disadvantage in this respect that the sealing edge formed by the transition between the two closing forces is beaten into the valve seat over the course of operation of the fuel injection valve, causing the hydraulically effective dealing line diameter to change over time, and hence the opening pressure does not remain constant. Particularly in modern fuel injection systems, which are optimized for low pollutant emissions, this is a major disadvantage.
- the fuel injection valve of the invention having the definitive characteristics of claim 1 , has the advantage over the prior art that the opening pressure of the fuel injection valve does not change in operation.
- the valve member has an end region in which two annular grooves are embodied.
- the first annular groove is disposed in a radial plane of the longitudinal axis of the valve member, and the second annular groove is offset axially toward the valve seat and is parallel to the first annular groove.
- the hydraulically effective sealing edge is formed at the transition from the first annular groove to the valve sealing face, whose diameter cannot change over the course of operation of the fuel injection valve.
- the annular land of the valve member that remains between the two annular grooves and whose outer jacket face forms the valve sealing face is embodied, on its outer edge, resiliently in the longitudinal direction of the valve member.
- the first annular groove is always in hydraulic communication with the pressure chamber.
- the hydraulic pressure in the first annular groove widens it elastically somewhat, so that the annular land of the valve member remaining between the two annular grooves is pressed against the valve seat when the opening stroke motion begins.
- This assures that the hydraulically effective sealing line diameter is always equivalent to the edge that is formed at the transition from the first annular groove to the valve sealing face. This is true regardless of angular tolerances when the valve is new and regardless of wear over the course of the service life.
- the edges embodied at the transition between the annular grooves and the valve sealing face are rounded or beveled. This lessens the notch effect caused by the pressing of these edges into the valve seat. As a consequence, better high-pressure stability is attained, and the resiliently embodied annular land of the valve sealing face is made capable of a rolling motion on the valve seat in the course of the opening or closing motion.
- FIG. 1 a longitudinal section through a fuel injection valve
- FIG. 2 an enlargement of the detail marked II in FIG. 1;
- FIG. 3 an enlargement of the detail marked III in FIG. 2.
- FIG. 1 a longitudinal section is shown through a fuel injection valve of the invention.
- a valve body 1 which forms part of a fuel injection system for internal combustion engines, has a bore 3 , in which a pistonlike valve member 5 that has a longitudinal axis 6 is disposed longitudinally displaceably.
- the closed end of the bore 3 is oriented toward the combustion chamber.
- the valve member 5 is guided sealingly in the bore 3 in a portion remote from the combustion chamber and is tapered toward the combustion chamber, forming a pressure shoulder 9 .
- the valve member 5 On its end toward the combustion chamber, the valve member 5 changes into a substantially conical end region 22 , which cooperates with a likewise conical valve seat 18 formed on the end of the bore 3 toward the combustion chamber.
- a pressure chamber 7 is formed at the level of the pressure shoulder 9 , and the pressure chamber continues, in the form of an annular conduit surrounding the valve member 5 , on as far as the valve seat 18 .
- the pressure chamber 7 Via an inlet conduit 4 embodied in the valve body 1 , the pressure chamber 7 communicates with a high-pressure fuel source, not shown in the drawing, enabling the pressure chamber to be filled with fuel at high pressure.
- Embodied on the valve member 5 between the pressure shoulder 9 and the end region 22 is a guide portion 10 , by which the valve member 5 is guided in a guide region 14 of the bore 3 .
- a plurality of recesses 12 are disposed on the guide portion 10 and distributed uniformly over the circumference of the valve member 5 , making the fuel flow possible.
- At least one injection opening 20 is embodied in the valve seat 18 , connecting the bore 3 to the combustion chamber of the engine. As a result of the longitudinal motion of the valve member 5 , the at least one injection opening 20 is uncovered or closed, so that under the control of the valve member 5 , fuel from the pressure chamber can reach the combustion chamber of the engine through the injection opening.
- valve member 5 moves away from the valve seat 18 , and the end region 22 lifts from the valve seat 18 .
- the pressure chamber 7 communicates with the injection openings 20 , and fuel flows past the valve member 5 to the injection openings 20 and from there into the combustion chamber of the engine. Reducing the fuel inflow causes the pressure in the pressure chamber 7 to drop again, so that as soon as the closing force on the valve member 5 predominates, the valve member 5 moves back into its closing position, in which its end region 22 takes its seat on the valve member 5 .
- valve member 5 Since the valve member 5 is guided both in the portion remote from the combustion chamber and in the guide portion 10 in the bore 3 , a precisely central position of the valve member 5 in the bore 3 is obtained on the valve seat 18 as well, thus assuring a symmetrical flow of fuel to the valve seat 18 .
- FIG. 2 an enlargement of FIG. 1 in a detail marked II is shown.
- the substantially conical end face 22 of the valve member 5 has a first annular groove 30 and a second annular groove 32 , and the second annular groove is offset axially relative to the first annular groove 30 , but the two annular grooves 30 , 32 are parallel to one another.
- the annular grooves 30 , 32 are each disposed at least approximately in a radial plane relative to the longitudinal axis 6 of the valve member 5 .
- the end region 22 of the valve member 5 is divided into three portions, forming a first conical face 24 , which directly adjoins the valve member 5 ; a valve sealing face 26 embodied between the two annular grooves 30 , 32 ; and a second conical face 28 , which forms the end toward the combustion chamber of the valve member 5 .
- the valve sealing face 26 is embodied on an annular land 27 that remains between the annular grooves 30 , 32 .
- the first conical face 24 , the valve sealing face 26 , and the second conical face 28 all have at least approximately the same cone angle, but the first conical face 24 and the second conical face 28 are set back somewhat, so that in the closing position of the valve member 5 , or in other words when the pressure chamber 7 is closed off from the injection openings 20 , only the valve sealing face 26 comes to rest on the valve seat 18 .
- This position is shown in FIG. 2. Because of the set-back first conical face 24 , the first annular groove 30 always remains in hydraulic communication with the pressure chamber 7 , since between the first conical face 24 and the valve seat 28 a gap always remains.
- FIG. 3 an enlargement of FIG. 2 in the region marked III is shown.
- the valve member 5 is in a slightly open state, and so the valve sealing face 26 does not rest on the valve seat 18 .
- the part of the end region 22 of the valve member 5 that is acted upon hydraulically by the pressure in the pressure chamber 7 corresponds to the first conical face 24 as far as the first edge 35 , which is formed at the transition from the first annular groove 30 to the valve sealing face 26 and which forms the sealing line.
- the hydraulic forces acting in the axial direction on the walls of the first annular groove 30 cancel one another out.
- the annular land 27 between the two annular grooves 30 ; 32 is embodied resiliently on its outer end, so that upon contact of the valve member 5 with the valve seat 18 , the valve sealing face 26 is deformed away from the combustion chamber somewhat, and consequently the sealing face 26 always rests optimally on the valve seat 18 .
- the deformation of the valve sealing face 26 can be so extensive that the second closing force 28 , in the closed state of the fuel injection valve, comes to rest on the valve seat 18 , which thus limits the deformation of the valve sealing face 26 . If the second conical face 28 covers the injection opening 20 , then between individual injections the space in the injection valve that communicates with the combustion chamber and is filled with fuel is minimized, with a favorable effect on pollutant emissions from the engine.
- the annular land 27 with the valve sealing face 26 embodied on it has a height D in the direction of the longitudinal axis 6 that must be such as to enable elastic deformations without sacrificing the stability of the valve sealing face 26 .
- the height D is therefore preferably from 0.3 mm to 0.5 mm, while the axial height of the annular grooves 30 , 32 is approximately 0.2 mm to 0.4 mm.
- the edges that define the valve sealing face 26 are embodied as rounded or beveled.
- the valve sealing face 26 can roll on the valve seat 18 , and as a result, the notch stresses that occur as the edges 35 , 37 are pressed into the valve seat 18 are minimized.
Abstract
A fuel injection valve for internal combustion engines, having a valve body (1), in which a pistonlike valve member (5) is longitudinally displaceably disposed in a bore (3). The valve member (5) is surrounded, over at least part of its length, by a pressure chamber (7) that can be filled with fuel. On its end toward the combustion chamber, a valve seat (18) is embodied in the bore (3), on which seat the valve member (5) comes to rest with a valve sealing face (26) in a closing position, so that the pressure chamber (7) is disconnected from at least one injection opening (20) located downstream of the valve sealing face (18). In the end region of the valve member (5), a first annular groove (30) an a second annular groove (32), parallel to it and disposed axially toward the valve seat (18), are embodied, and the valve sealing face (26) is disposed between these two annular grooves (30; 32).
Description
- The invention is based on a fuel injection valve for internal combustion engines of the kind known for instance from German Patent Disclosure DE 196 18 650 A1. Such a fuel injection valve has a valve body, in which a bore is embodied. A pistonlike valve member is disposed longitudinally displaceably in this bore and on its end toward the combustion chamber has a valve sealing face, which cooperates with a valve seat embodied on the end of the bore toward the combustion chamber. The valve member is surrounded by a pressure chamber embodied in the valve body, and this pressure chamber can be filled with fuel at high pressure and extends as far as the valve seat. At least one injection opening is embodied in the valve seat, which connects the bore and thus the pressure chamber with the combustion chamber of the engine. By means of a longitudinal motion of a valve member, the valve member with its valve sealing face lifts from the valve seat, causing the pressure chamber to communicate with the injection openings. The valve seat is embodied essentially conically, and the tip of the cone forming the conical face is oriented toward the combustion chamber. The valve sealing face of the valve member is correspondingly embodied conically as well, and the valve sealing face has two conical faces with different angles of inclination, so that at the transition between these two conical faces, a sealing edge is formed. In the closing position of the valve member, or in other words when the valve sealing face is resting on the valve seat, this sealing edge is pressed into the valve seat, so that secure sealing off of the pressure chamber from the injection openings is possible.
- The valve member is acted upon by a device with a closing force that presses the valve member onto the valve seat. Because of the hydraulic pressure in the pressure chamber, the valve member experiences a force acting in the axial direction, which force is oriented counter to the closing force. If the pressure in the pressure chamber exceeds an opening pressure, then the hydraulic force on the valve member becomes greater than the closing force, and the valve member moves out of its closing position, away from the valve seat. The magnitude of this opening pressure depends, among other factors, on what the diameter of the sealing edge at the valve seat is. A change in the opening pressure causes a change in the injection characteristic of the injection valve, so that for optimal injection, an at least approximately constant opening pressure is indispensable. The known fuel injection valve has the disadvantage in this respect that the sealing edge formed by the transition between the two closing forces is beaten into the valve seat over the course of operation of the fuel injection valve, causing the hydraulically effective dealing line diameter to change over time, and hence the opening pressure does not remain constant. Particularly in modern fuel injection systems, which are optimized for low pollutant emissions, this is a major disadvantage.
- The fuel injection valve of the invention, having the definitive characteristics of
claim 1, has the advantage over the prior art that the opening pressure of the fuel injection valve does not change in operation. To that end, the valve member has an end region in which two annular grooves are embodied. The first annular groove is disposed in a radial plane of the longitudinal axis of the valve member, and the second annular groove is offset axially toward the valve seat and is parallel to the first annular groove. This divides the end region of the valve member into three portions, and the valve sealing face is embodied at an annular land that remains between the two annular grooves. The hydraulically effective sealing edge is formed at the transition from the first annular groove to the valve sealing face, whose diameter cannot change over the course of operation of the fuel injection valve. - In an advantageous feature of the subject of the invention, the annular land of the valve member that remains between the two annular grooves and whose outer jacket face forms the valve sealing face is embodied, on its outer edge, resiliently in the longitudinal direction of the valve member. As a result, the valve sealing face can adapt optimally to the valve seat, so that even in the time just before the injection, when because of the rising pressure in the pressure chamber the valve body is widened elastically to some extent, an optimal contact of the valve sealing face with the valve seat is accomplished.
- In another feature of the subject of the invention, the first annular groove is always in hydraulic communication with the pressure chamber. The hydraulic pressure in the first annular groove widens it elastically somewhat, so that the annular land of the valve member remaining between the two annular grooves is pressed against the valve seat when the opening stroke motion begins. This assures that the hydraulically effective sealing line diameter is always equivalent to the edge that is formed at the transition from the first annular groove to the valve sealing face. This is true regardless of angular tolerances when the valve is new and regardless of wear over the course of the service life.
- In a further advantageous feature, the edges embodied at the transition between the annular grooves and the valve sealing face are rounded or beveled. This lessens the notch effect caused by the pressing of these edges into the valve seat. As a consequence, better high-pressure stability is attained, and the resiliently embodied annular land of the valve sealing face is made capable of a rolling motion on the valve seat in the course of the opening or closing motion.
- Further advantages and advantageous features of the subject of the invention can be learned from the drawing, the description, and the claims.
- One exemplary embodiment of the fuel injection valve of the invention is shown in the drawing. Shown are
- FIG. 1, a longitudinal section through a fuel injection valve;
- FIG. 2, an enlargement of the detail marked II in FIG. 1; and
- FIG. 3, an enlargement of the detail marked III in FIG. 2.
- In FIG. 1, a longitudinal section is shown through a fuel injection valve of the invention. A
valve body 1, which forms part of a fuel injection system for internal combustion engines, has abore 3, in which apistonlike valve member 5 that has alongitudinal axis 6 is disposed longitudinally displaceably. In the installed state of the fuel injection valve in the engine, the closed end of thebore 3 is oriented toward the combustion chamber. Thevalve member 5 is guided sealingly in thebore 3 in a portion remote from the combustion chamber and is tapered toward the combustion chamber, forming apressure shoulder 9. On its end toward the combustion chamber, thevalve member 5 changes into a substantiallyconical end region 22, which cooperates with a likewiseconical valve seat 18 formed on the end of thebore 3 toward the combustion chamber. By means of a radial enlargement of thebore 3, apressure chamber 7 is formed at the level of thepressure shoulder 9, and the pressure chamber continues, in the form of an annular conduit surrounding thevalve member 5, on as far as thevalve seat 18. Via aninlet conduit 4 embodied in thevalve body 1, thepressure chamber 7 communicates with a high-pressure fuel source, not shown in the drawing, enabling the pressure chamber to be filled with fuel at high pressure. Embodied on thevalve member 5 between thepressure shoulder 9 and theend region 22 is aguide portion 10, by which thevalve member 5 is guided in aguide region 14 of thebore 3. To assure the flow of fuel from thepressure chamber 7 to thevalve seat 18, a plurality ofrecesses 12, for instance four of them, are disposed on theguide portion 10 and distributed uniformly over the circumference of thevalve member 5, making the fuel flow possible. At least one injection opening 20 is embodied in thevalve seat 18, connecting thebore 3 to the combustion chamber of the engine. As a result of the longitudinal motion of thevalve member 5, the at least one injection opening 20 is uncovered or closed, so that under the control of thevalve member 5, fuel from the pressure chamber can reach the combustion chamber of the engine through the injection opening. - The control of the injection activity of the fuel injection valve is accomplished by hydraulic forces. An injection cycle looks like this: By a device not shown in the drawing, the
valve member 5 is acted upon by a closing force that presses thevalve member 5 with itsend region 22 onto thevalve seat 18. As a result, thepressure chamber 7 is closed off from the injection openings, and no fuel reaches the combustion chamber of the engine through the injection openings. Introducing fuel at high pressure through theinlet conduit 4 into thepressure chamber 7 results in a hydraulic force in the longitudinal direction of thevalve member 5 from action on thepressure shoulder 5 and at least some parts of theend region 22. If these hydraulic forces exceed the closing force on the valve member, thevalve member 5 moves away from thevalve seat 18, and theend region 22 lifts from thevalve seat 18. As a result, thepressure chamber 7 communicates with theinjection openings 20, and fuel flows past thevalve member 5 to theinjection openings 20 and from there into the combustion chamber of the engine. Reducing the fuel inflow causes the pressure in thepressure chamber 7 to drop again, so that as soon as the closing force on thevalve member 5 predominates, thevalve member 5 moves back into its closing position, in which itsend region 22 takes its seat on thevalve member 5. Since thevalve member 5 is guided both in the portion remote from the combustion chamber and in theguide portion 10 in thebore 3, a precisely central position of thevalve member 5 in thebore 3 is obtained on thevalve seat 18 as well, thus assuring a symmetrical flow of fuel to thevalve seat 18. - In FIG. 2, an enlargement of FIG. 1 in a detail marked II is shown. The substantially
conical end face 22 of thevalve member 5 has a firstannular groove 30 and a secondannular groove 32, and the second annular groove is offset axially relative to the firstannular groove 30, but the twoannular grooves annular grooves longitudinal axis 6 of thevalve member 5. As a result, theend region 22 of thevalve member 5 is divided into three portions, forming a firstconical face 24, which directly adjoins thevalve member 5; avalve sealing face 26 embodied between the twoannular grooves conical face 28, which forms the end toward the combustion chamber of thevalve member 5. Thevalve sealing face 26 is embodied on anannular land 27 that remains between theannular grooves conical face 24, thevalve sealing face 26, and the secondconical face 28 all have at least approximately the same cone angle, but the firstconical face 24 and the secondconical face 28 are set back somewhat, so that in the closing position of thevalve member 5, or in other words when thepressure chamber 7 is closed off from theinjection openings 20, only thevalve sealing face 26 comes to rest on thevalve seat 18. This position is shown in FIG. 2. Because of the set-back firstconical face 24, the firstannular groove 30 always remains in hydraulic communication with thepressure chamber 7, since between the firstconical face 24 and the valve seat 28 a gap always remains. - In FIG. 3, an enlargement of FIG. 2 in the region marked III is shown. Here the
valve member 5 is in a slightly open state, and so thevalve sealing face 26 does not rest on thevalve seat 18. The part of theend region 22 of thevalve member 5 that is acted upon hydraulically by the pressure in thepressure chamber 7 corresponds to the firstconical face 24 as far as thefirst edge 35, which is formed at the transition from the firstannular groove 30 to thevalve sealing face 26 and which forms the sealing line. The hydraulic forces acting in the axial direction on the walls of the firstannular groove 30 cancel one another out. Since theannular grooves 30; 32 are cut into theend region 22 of thevalve member 5, theannular land 27 between the twoannular grooves 30; 32 is embodied resiliently on its outer end, so that upon contact of thevalve member 5 with thevalve seat 18, thevalve sealing face 26 is deformed away from the combustion chamber somewhat, and consequently the sealingface 26 always rests optimally on thevalve seat 18. The deformation of thevalve sealing face 26 can be so extensive that thesecond closing force 28, in the closed state of the fuel injection valve, comes to rest on thevalve seat 18, which thus limits the deformation of thevalve sealing face 26. If the secondconical face 28 covers the injection opening 20, then between individual injections the space in the injection valve that communicates with the combustion chamber and is filled with fuel is minimized, with a favorable effect on pollutant emissions from the engine. - The
annular land 27 with thevalve sealing face 26 embodied on it has a height D in the direction of thelongitudinal axis 6 that must be such as to enable elastic deformations without sacrificing the stability of thevalve sealing face 26. The height D is therefore preferably from 0.3 mm to 0.5 mm, while the axial height of theannular grooves - Besides the exemplary embodiment shown in FIG. 3, it may also be provided that the edges that define the
valve sealing face 26, that is, thefirst edge 35 remote from the combustion chamber and thesecond edge 37 toward the combustion chamber, are embodied as rounded or beveled. As a result, in the opening motion of thevalve member 5, thevalve sealing face 26 can roll on thevalve seat 18, and as a result, the notch stresses that occur as theedges valve seat 18 are minimized.
Claims (5)
1. A fuel injection valve for internal combustion engines, having a valve body (1), in which a pistonlike valve member (5) is longitudinally displaceably disposed in a bore (3), and the valve member (5) is surrounded, over at least part of its length, by a pressure chamber (7) that can be filled with fuel, and having a valve seat (18), embodied on the end toward the combustion chamber of the bore (3), on which seat the valve member (5) comes to rest with a valve sealing face (26) in a closing position, so that the pressure chamber (7) is disconnected from at least one injection opening (20) located downstream of the valve sealing face (18), characterized in that a first annular groove (30) an a second annular groove (32), parallel to it and disposed axially toward the valve seat (18), are embodied in the end region of the valve member (5) toward the combustion chamber, and that the valve sealing face (26) is disposed on an annular land (27) that remains between these two annular grooves (30; 32).
2. The fuel injection valve of claim 1 , characterized in that the valve sealing face (26) is shaped at least approximately conically.
3. The fuel injection valve of claim 1 , characterized in that the annular land (27) of the valve member (5) that remains between the annular grooves (30; 32) is embodied, on its outer edge, resiliently in the direction of motion of the valve member (5).
4. The fuel injection valve of claim 1 , characterized in that the first annular groove (30) is constantly in hydraulic communication with the pressure chamber (7).
5. The fuel injection valve of claim 1 , characterized in that the edges (35; 37) formed at the transition from the annular grooves (30; 32) to the valve sealing face (26) are rounded or beveled.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10115216.7 | 2001-03-28 | ||
DE10115216A DE10115216A1 (en) | 2001-03-28 | 2001-03-28 | Fuel injection valve for internal combustion engines |
PCT/DE2002/001091 WO2002077445A1 (en) | 2001-03-28 | 2002-03-26 | Fuel-injection valve for internal combustion engines |
Publications (2)
Publication Number | Publication Date |
---|---|
US20030173428A1 true US20030173428A1 (en) | 2003-09-18 |
US6923388B2 US6923388B2 (en) | 2005-08-02 |
Family
ID=7679340
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/296,712 Expired - Fee Related US6923388B2 (en) | 2001-03-28 | 2002-03-26 | Fuel-injection valve for internal combustion engines |
Country Status (5)
Country | Link |
---|---|
US (1) | US6923388B2 (en) |
EP (1) | EP1373715B1 (en) |
JP (1) | JP2004518890A (en) |
DE (2) | DE10115216A1 (en) |
WO (1) | WO2002077445A1 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1559903A1 (en) * | 2004-01-28 | 2005-08-03 | Siemens VDO Automotive S.p.A. | Fuel injector with deformable needle |
EP1559905A1 (en) * | 2004-01-29 | 2005-08-03 | Siemens VDO Automotive S.p.A. | Fluid injector with a deformable valve needle |
WO2005106238A1 (en) * | 2004-04-30 | 2005-11-10 | Siemens Aktiengesellschaft | Nozzle assembly group and valve |
US20070063074A1 (en) * | 2003-05-19 | 2007-03-22 | Jochen Mertens | Fuel injection valve for internal combustion engines |
US20120180757A1 (en) * | 2009-09-21 | 2012-07-19 | Wolfgang Gerber | Fuel injection valve for an internal combustion engine |
CN107143452A (en) * | 2017-07-17 | 2017-09-08 | 辽阳新风科技有限公司 | A kind of oil nozzle couple, fuel injector and automobile |
CN112282999A (en) * | 2020-10-30 | 2021-01-29 | 安徽江淮汽车集团股份有限公司 | Can reduce sprayer structure of sound of taking a seat |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10245573A1 (en) * | 2002-09-27 | 2004-04-08 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
DE10259169A1 (en) * | 2002-12-18 | 2004-07-01 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
CA2662123C (en) * | 2006-08-30 | 2015-12-01 | Jagotec Ag | Controlled release oral dosage formulations comprising a core and one or more barrier layers |
WO2012085901A2 (en) * | 2011-05-09 | 2012-06-28 | Lietuvietis Vilis I | Valve covered orifice pressure equalizing channel |
DE102016203028A1 (en) * | 2016-02-26 | 2017-08-31 | Bayerische Motoren Werke Aktiengesellschaft | fuel injector |
US11746734B2 (en) * | 2018-08-23 | 2023-09-05 | Progress Rail Services Corporation | Electronic unit injector shuttle valve |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1952816A (en) * | 1931-04-04 | 1934-03-27 | Bendix Res Corp | Fuel injector |
US4060199A (en) * | 1975-10-01 | 1977-11-29 | Robert Bosch G.M.B.H. | Electromagnetic fuel injection valve |
US4995559A (en) * | 1987-06-26 | 1991-02-26 | Hitachi, Ltd. | Electromagnetic fuel injection valve |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19618650B4 (en) | 1996-05-09 | 2006-04-27 | Robert Bosch Gmbh | Method for producing a fuel injection valve for internal combustion engines |
DE19844638A1 (en) * | 1998-09-29 | 2000-03-30 | Siemens Ag | Fuel injection valve for an internal combustion engine |
DE19931891A1 (en) * | 1999-07-08 | 2001-01-18 | Siemens Ag | Fuel-injection valve for combustion engine |
DE19944638A1 (en) | 1999-09-17 | 2001-03-22 | Hettich Paul Gmbh & Co | Fastening arrangement |
-
2001
- 2001-03-28 DE DE10115216A patent/DE10115216A1/en not_active Withdrawn
-
2002
- 2002-03-26 WO PCT/DE2002/001091 patent/WO2002077445A1/en active IP Right Grant
- 2002-03-26 DE DE50201953T patent/DE50201953D1/en not_active Expired - Lifetime
- 2002-03-26 US US10/296,712 patent/US6923388B2/en not_active Expired - Fee Related
- 2002-03-26 EP EP02727266A patent/EP1373715B1/en not_active Expired - Lifetime
- 2002-03-26 JP JP2002575467A patent/JP2004518890A/en active Pending
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1952816A (en) * | 1931-04-04 | 1934-03-27 | Bendix Res Corp | Fuel injector |
US4060199A (en) * | 1975-10-01 | 1977-11-29 | Robert Bosch G.M.B.H. | Electromagnetic fuel injection valve |
US4995559A (en) * | 1987-06-26 | 1991-02-26 | Hitachi, Ltd. | Electromagnetic fuel injection valve |
US5098016A (en) * | 1987-06-26 | 1992-03-24 | Hitachi, Ltd. | Electromagnetic fuel injection valve |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20070063074A1 (en) * | 2003-05-19 | 2007-03-22 | Jochen Mertens | Fuel injection valve for internal combustion engines |
EP1559903A1 (en) * | 2004-01-28 | 2005-08-03 | Siemens VDO Automotive S.p.A. | Fuel injector with deformable needle |
WO2005075812A1 (en) * | 2004-01-28 | 2005-08-18 | Siemens Vdo Automotive Spa | Fluid injector with deformable needle |
EP1559905A1 (en) * | 2004-01-29 | 2005-08-03 | Siemens VDO Automotive S.p.A. | Fluid injector with a deformable valve needle |
WO2005106238A1 (en) * | 2004-04-30 | 2005-11-10 | Siemens Aktiengesellschaft | Nozzle assembly group and valve |
US20120180757A1 (en) * | 2009-09-21 | 2012-07-19 | Wolfgang Gerber | Fuel injection valve for an internal combustion engine |
US9297344B2 (en) * | 2009-09-21 | 2016-03-29 | Continental Automotive Gmbh | Fuel injection valve for an internal combustion engine |
CN107143452A (en) * | 2017-07-17 | 2017-09-08 | 辽阳新风科技有限公司 | A kind of oil nozzle couple, fuel injector and automobile |
CN112282999A (en) * | 2020-10-30 | 2021-01-29 | 安徽江淮汽车集团股份有限公司 | Can reduce sprayer structure of sound of taking a seat |
Also Published As
Publication number | Publication date |
---|---|
US6923388B2 (en) | 2005-08-02 |
WO2002077445A1 (en) | 2002-10-03 |
EP1373715B1 (en) | 2005-01-05 |
DE50201953D1 (en) | 2005-02-10 |
DE10115216A1 (en) | 2002-10-10 |
EP1373715A1 (en) | 2004-01-02 |
JP2004518890A (en) | 2004-06-24 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US6827297B2 (en) | Fuel injection valve for internal combustion engines | |
US6257506B1 (en) | Fuel injector for auto-ignition internal combustion engines | |
US5890660A (en) | Fuel injection nozzle | |
US6923388B2 (en) | Fuel-injection valve for internal combustion engines | |
US5743470A (en) | Fuel injection valve for internal combustion engines | |
US6789783B2 (en) | Fuel injection valve for internal combustion engines | |
US6669117B2 (en) | Fuel injection valve for internal combustion engines | |
US20080296411A1 (en) | Fuel Injection Valve for an Internal Combustion Engine | |
EP1136693B1 (en) | Plug pin for an internal combustion engine fuel injector nozzle | |
US8720802B2 (en) | Fuel injection valve for internal combustion engines | |
US20080240952A1 (en) | High-Pressure Pump, in Particular for a Fuel Injection System of an Internal Combustion Engine | |
US20020033423A1 (en) | Common rail injector | |
US20070120087A1 (en) | Valve body with multiconical geometry at the valve seat | |
US7077340B2 (en) | Fuel injection valve for internal combustion engines | |
US20060011749A1 (en) | Fuel injection valve for internal combustion engines | |
US7100847B2 (en) | Fuel injection valve for internal combustion engines | |
US20050205693A1 (en) | Fuel injection valve for internal combustion engines | |
EP0844383B1 (en) | Injector | |
US5755385A (en) | Fuel-injection valve for internal combustion engines | |
US6874704B2 (en) | Fuel-injection valve for internal combustion engines | |
US7044406B2 (en) | Fuel injection valve for an internal combustion engine | |
US20070063074A1 (en) | Fuel injection valve for internal combustion engines | |
US6113011A (en) | Fuel injection valve for internal combustion engines | |
US20040195350A1 (en) | Fuel injection valve | |
US6502554B1 (en) | Fuel injection valve for internal combustion engines |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: ROBERT BOSCH GMBH, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:BUEHLER, CHRISTOPH;REEL/FRAME:014080/0680 Effective date: 20030205 |
|
REMI | Maintenance fee reminder mailed | ||
LAPS | Lapse for failure to pay maintenance fees | ||
STCH | Information on status: patent discontinuation |
Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362 |
|
FP | Lapsed due to failure to pay maintenance fee |
Effective date: 20090802 |